US12264989B2 - Wheel test device with rail wheel to contact test wheel while test wheel is rotatably supported - Google Patents

Wheel test device with rail wheel to contact test wheel while test wheel is rotatably supported Download PDF

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Publication number
US12264989B2
US12264989B2 US18/048,319 US202218048319A US12264989B2 US 12264989 B2 US12264989 B2 US 12264989B2 US 202218048319 A US202218048319 A US 202218048319A US 12264989 B2 US12264989 B2 US 12264989B2
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wheel
test
electric motor
rail
torque
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US20230054417A1 (en
Inventor
Sigeru Matsumoto
Hiroshi Miyashita
Kazuhiro Murauchi
Shuichi Tokita
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Kokusai Keisokuki KK
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Kokusai Keisokuki KK
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Assigned to KOKUSAI KEISOKUKI KABUSHIKI KAISHA reassignment KOKUSAI KEISOKUKI KABUSHIKI KAISHA ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: TOKITA, SHUICHI, MATSUMOTO, SIGERU, MIYASHITA, HIROSHI, MURAUCHI, KAZUHIRO
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    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M17/00—Testing of vehicles
    • G01M17/08—Railway vehicles
    • G01M17/10—Suspensions, axles or wheels
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M99/00—Subject matter not provided for in other groups of this subclass
    • G01M99/004—Testing the effects of speed or acceleration
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M99/00—Subject matter not provided for in other groups of this subclass
    • G01M99/007—Subject matter not provided for in other groups of this subclass by applying a load, e.g. for resistance or wear testing

Definitions

  • aspects of the present disclosure relate to a wheel test device.
  • test device for simulating and examining an interaction between a rail and a wheel during when a railway vehicle is running.
  • a test device capable of performing a test simulating a running state of a railway vehicle by rotating both a rail wheel which is a disk-shaped member having a cross-sectional shape simulating a rail at an outer peripheral portion thereof and a wheel in a state where the wheel is pressed against the rail wheel.
  • the conventional test device mentioned above is driven by a single electric motor, when performing a test for applying a large torque to the wheel while rotating the wheel at a high speed, it is necessary to use a large-capacity electric motor, and thus there is a problem that power consumption during the test becomes enormous.
  • At least one aspects of the present disclosure are advantageous to provide a technique to reduce power consumption of a wheel test device.
  • a wheel test device including a rail wheel support configured to rotatably support a rail wheel, a wheel support configured to rotatably support a test wheel in a state where the test wheel is in contact with the rail wheel, a first electric motor configured to rotate the rail wheel and the test wheel, a power distributor configured to distribute power generated by the first electric motor to the rail wheel and the test wheel, and a torque generator configured to generate torque to be applied to the test wheel.
  • the torque generator includes a rotating frame rotationally driven by the first electric motor, and a second electric motor mounted on the rotating frame. The rail wheel, the test wheel, or both the rail wheel and the test wheel is connected to the first electric motor via the torque generator.
  • the rail wheel and the test wheel are configured to rotate in opposite directions at substantially the same peripheral speed when the operation of the second electric motor is stopped.
  • a rated output of the second electric motor is equal to or more than 3 kW, and moment of inertia of a rotating part of the second electric motor is equal to or less than 0.01 kg ⁇ m 2 .
  • FIG. 1 is a perspective view of a wheel test device.
  • FIG. 2 is a perspective view of the wheel test device.
  • FIG. 3 is a plan view of the wheel test device.
  • FIG. 4 is a block diagram showing a schematic configuration of a drive system.
  • FIG. 5 is a cross-sectional view showing a schematic configuration of a gear box.
  • FIG. 6 is a cross-sectional view showing a schematic configuration of a torque generator and its periphery.
  • FIG. 7 is a cross-sectional view showing a schematic configuration of a second electric motor.
  • FIG. 8 is a block diagram showing a schematic configuration of a control system.
  • FIG. 9 is a plan view showing a schematic configuration of another wheel test device.
  • FIG. 10 is a front view showing a schematic configuration of the wheel test device shown in FIG. 9 .
  • FIGS. 1 and 2 are perspective views of a wheel test device 1 according to a first embodiment of the present disclosure.
  • FIG. 1 is a front side view and
  • FIG. 2 is a rear side view.
  • FIG. 3 is a plan view of the wheel test device 1 .
  • a direction from lower right to upper left is defined as an X-axis direction
  • a direction from upper right to lower left is defined as a Y-axis direction
  • a direction from bottom to top is defined as a Z-axis direction.
  • the X-axis direction and the Y-axis direction are horizontal directions orthogonal to each other, and the Z-axis direction is a vertical direction.
  • Arbitrary straight lines respectively extending in the X-axis direction, the Y-axis direction, and the Z-axis direction are referred to as an X-axis, a Y-axis, and a Z-axis, respectively.
  • the X-axis positive direction is referred to as left
  • the X-axis negative direction is referred to as right
  • the Y-axis positive direction is referred to as front
  • the Y-axis negative direction is referred to as rear
  • the Z-axis positive direction is referred to as up
  • the Z-axis negative direction is referred to as down.
  • the wheel test device 1 is a device capable of simulating an interaction between a rail and a wheel that occurs when a railway vehicle is running, and evaluating, for example, an adhesion property and the like between the rail and the wheel.
  • a rail wheel R of which outer periphery having a cross-sectional shape that simulates a rail head is used, and both the rail wheel R and a wheel for tests (hereinafter referred to as a “test wheel W”) are rotated in a state where the test wheel W is pressed against the rail wheel R, whereby the interaction between the rail and the wheel when a railway vehicle is running is simulated.
  • the wheel test device 1 includes a drive system DS that drives the rail wheel R and the test wheel W.
  • FIG. 4 is a block diagram showing a schematic configuration of the drive system DS.
  • the drive system DS includes an actuating section AS that generates mechanical power (hereinafter simply referred to as “power”) and a transmitting section TS that transmits the power generated by the actuating section AS to the rail wheel R and the test wheel W which are targets to be driven, and constitutes a power circulation system together with the rail wheel R and the test wheel W, as will be described later.
  • the actuating section AS includes a rotary driver 10 (a speed control drive device) capable of controlling rotation speed of a driven object, and a torque generator 20 (a torque control drive device) capable of controlling torque to be applied to the driven object.
  • a rotary driver 10 a speed control drive device
  • a torque generator 20 a torque control drive device capable of controlling torque to be applied to the driven object.
  • the drive system DS of the present embodiment by adopting a configuration in which drive control is divided into speed control and torque control and dedicated drivers perform speed control and torque control, respectively, it is made possible to drive at high speed (or at high acceleration) and high torque while using a motor having a relatively small capacity. Furthermore, the drive system DS employs a power circulation system, thereby realizing a higher energy utilization efficiency than those of the conventional devices.
  • the transmitting section TS includes a first transmission section 30 and a second transmission section 40 .
  • the torque generator 20 also constitutes a part of the transmitting section TS.
  • the first transmission section 30 transmits rotation output from the rotary driver 10 to the rail wheel R and the torque generator 20 .
  • the torque generator 20 adds power generated by the torque generator 20 itself to the power transmitted from the rotary driver 10 and outputs the added power.
  • the second transmission section 40 transmits the output of the torque generator 20 to the test wheel W.
  • the rail wheel R and the test wheel W are attached to the wheel test device 1 so that they are arranged in the radial direction with their rotation axes parallel to each other.
  • the test wheel W is pressed against the rail wheel R, and the test wheel W and the rail wheel R are driven to rotate in directions opposite to each other at substantially the same peripheral speed (i.e., a linear speed of an outer peripheral surface) in a state where an outer peripheral surface (tread surface) of the test wheel W is in contact with an outer peripheral surface (top surface) of the rail wheel R.
  • the transmitting section TS together with the test wheel W and the rail wheel R constitutes a power circulation system (i.e., a loop of power transmission shafts).
  • the torque generator 20 applies torque to the power circulation system by giving a phase difference between an input shaft (first transmission section 30 ) and an output shaft (second transmission section 40 ).
  • the wheel test device 1 can apply torque (or tangential force) to the test wheel W without substantially absorbing the generated power, and thus the wheel test device 1 can be operated with relatively little energy consumption.
  • the first transmission section 30 of the present embodiment is configured so that the rail wheel R and the test wheel W are rotationally driven at the same peripheral speed in opposite directions with respect to each other in a state where the operation of the torque generator 20 (specifically, the second electric motor 22 described later) is stopped. It should be noted that a configuration may be adopted in which a difference in peripheral speed occurs between the rail wheel R and the test wheel W in a state where the operation of the torque generator 20 is stopped. However, in this case, since the amount of operation of the torque generator 20 increases in order to compensate for the difference in peripheral speed, the energy consumption increases.
  • first transmission section 30 of the present embodiment is configured so that the rail wheel R and the torque generator 20 are rotationally driven at the same rotation speed
  • a configuration may be adopted in which the rail wheel R and the torque generator 20 are rotated at different rotation speeds as long as the rail wheel R and the test wheel W are rotationally driven at substantially the same peripheral speed.
  • the rotary driver 10 includes a tension adjustment table 11 and a first electric motor 12 (a speed control motor) installed on the tension adjustment table 11 .
  • the first electric motor 12 of the present embodiment is a so-called inverter motor whose drive is controlled by an inverter, but another type of motor, such as a servo motor or a stepping motor, in which rotation speed can be controlled, may be used for the first electric motor 12 .
  • the rotary driver 10 may include a reducer configured to reduce the rotation output from the first electric motor 12 .
  • the tension adjustment table 11 will be described later.
  • the first transmission section 30 includes a first belt mechanism 31 , a rail wheel support 32 , a shaft 33 , and a gear box 34 (gear device).
  • the first belt mechanism 31 includes a drive pulley 311 driven by the rotary driver 10 , a driven pulley 312 attached to an input shaft (one of shafts 321 described later) of the rail wheel support 32 , and a belt 313 wound around the drive pulley 311 and the driven pulley 312 .
  • the rotation output from the rotary driver 10 is transmitted to the rail wheel support 32 by the first belt mechanism 31 of the first transmission section 30 .
  • the belt 313 of the present embodiment is a V-ribbed belt having a plurality of V-shaped ribs arranged in a width direction, but may be another type of belt such as a V-belt having a trapezoidal cross-sectional shape, a toothed belt, a flat belt, or a round belt.
  • the first belt mechanism 31 of the present embodiment includes a single belt transmission system including a drive pulley 311 , a driven pulley 312 , and a belt 313 , but may include two or more belt transmission systems connected in parallel or in series.
  • the transmission from the rotary driver 10 to the rail wheel support 32 is not limited to belt transmission, but other types of winding transmission such as chain transmission or wire transmission, or other transmission systems such as gear transmission may be used.
  • the rotary driver 10 and the rail wheel support 32 may be disposed coaxially (i.e., so that the rotation axes or the center lines are coincident with each other) and an output shaft of the rotary driver 10 and an input shaft of the rail wheel support 32 may be directly connected to each other.
  • the tension adjustment table 11 of the rotary driver 10 includes a fixed frame 111 fixed to a base B and a movable frame 112 to which the rotary driver 10 is attached.
  • the movable frame 112 is pivotally connected to the fixed frame 111 via a rod 114 R extending in the Y-axis direction at a right end portion of the movable frame 112 , so that an inclination around the Y-axis can be adjusted.
  • a distance between the drive pulley 311 FIG.
  • the driven pulley 312 can be changed by changing the inclination of the movable frame 112 , whereby it is made possible to adjust the tension of the belt 313 wound around the drive pulley 311 and the driven pulley 312 .
  • the rail wheel support 32 includes a pair of bearings 322 and a pair of shafts 321 .
  • the pair of bearings 322 are arranged across the rail wheel R, in front of and behind the rail wheel R (i.e., arranged in the Y-axis direction), with the rotation axes thereof oriented the Y-axis direction, and are coaxially arranged.
  • One shaft 321 is rotatably supported by the front bearing 322 , and the other shaft 321 is rotatably supported by the rear bearing 322 .
  • the shafts 321 are flanged shafts each provided with a flange configured for mounting the rail wheel R at one end thereof, and are removably and coaxially mounted on respective side surfaces of the rail wheel R by bolts.
  • the driven pulley 312 of the first belt mechanism 31 is attached to the other end of the front shaft 321 .
  • One end of the shaft 33 is connected to the other end of the rear shaft 321 .
  • the other end of the shaft 33 is connected to an input shaft 342 a of the gear box 34 .
  • the rail wheel support 32 (specifically, the shafts 321 ) functions as a power distributor configured to distribute the power generated by the first electric motor 12 and transmitted by the first belt mechanism 31 to the rail wheel R and the shaft 33 (and finally to the test wheel W).
  • the coupling structure between the shafts 321 and the rail wheel R is not limited to the coupling by the flange, but may be another coupling structure such as, for example, a structure in which the shaft 321 is fitted into a through hole provided at the center of the rail wheel R.
  • the shaft 221 is rotatably supported by the pair of bearings 225 and 227 .
  • One end (the right end in FIG. 7 ) of the shaft 221 protrudes to the outside through the flange 224 and the bearing 225 and serves as an output shaft of the second electric motor 22 .
  • the other end (the left end in FIG. 7 ) of the shaft 221 is connected to the rotary encoder RE.
  • the controller 70 controls the driving of the second electric motor 22 of the torque generator 20 so that the torque of the test wheel W becomes 0. Then, the controller 70 controls the first electric motor 12 of the rotary driver 10 to gradually reduce the rotation speed of the rail wheel R to stop the rotation, and then drives the motor 531 of the wheel load applying mechanism 53 to move the test wheel W away from the rail wheel R by a predetermined distance to end the test.
  • the lateral pressure applying mechanism 54 is a mechanism that applies lateral pressure (thrust load) to the test wheel W.
  • the lateral pressure includes lateral creep force (a component of adhesive force in the axial direction of the test wheel W) and flange reaction force (force caused by a contact between a flange of the test wheel W and a gauge corner of the rail wheel R), and the latter flange reaction force is applied (or adjusted to a predetermined value) by the lateral pressure applying mechanism 54 .
  • the motor 542 is connected to the controller 70 via a servo amplifier 542 a .
  • the lateral pressure detector 544 is connected to the measuring engine 80 via an amplifier 544 a .
  • Phase information of the shaft detected by the rotary encoder RE embedded in the motor 542 is input to the controller 70 through the servo amplifier 542 a.
  • the cant angle applying mechanism 55 includes a curved guide 553 that supports the second movable base 522 B at an outer peripheral portion apart from the rotation axis A 1 so that the second movable base 522 B can swing about the rotation axis A 1 with respect to the first movable base 522 A.
  • the curved guide 553 is a guideway type circulating rolling bearing including a curved rail (guideway) and a carriage capable of running on the rail via rolling elements, but other types of curved guide mechanism may be used as the curved guide 553 .
  • the cant angle applying mechanism 55 includes a motor 554 ( FIG. 9 ) and a motion converter 555 that converts rotational motion of the motor 554 into a linear motion in the Y-axis direction.
  • the motor 554 in the present embodiment is an AC servo motor, other types of motor capable of controlling driving amount (rotation angle), such as a DC servo motor or a stepping motor, may be used as the motor 554 .
  • the motion converter 555 in the present embodiment is a feed screw mechanism such as a ball screw, other types of motion converter may be used.
  • the motor 554 is connected to the controller 70 via a servo amplifier 554 a .
  • Phase information of the shaft detected by a rotary encoder RE embedded in the motor 554 is input to the controller 70 through the servo amplifier 554 a.
  • the attack angle applying mechanism 56 is a mechanism having a function of applying an attack angle to the test wheel W.
  • the attack angle is an angle formed between the rail and the wheel, and more specifically, an angle about a vertical axis (i.e., an angle in the yawing direction) formed between a width direction of the rail (railroad tie direction) and the axial direction of the wheel.
  • the attack angle is defined as an angle between the rotation axis of the rail wheel R and the rotation axis of the test wheel W about the X axis.
  • a support frame 1523 of the wheel support 1500 of the present embodiment includes a box-shaped support column 1523 a fixed to the third movable base 522 C, and an arm 1523 b connected to the support column 1523 a so as to be rotatable about a rotation axis A 2 extending in the X-axis direction.
  • the arm 1523 b is a substantially L-shaped member as seen from above, and includes a base part 1523 b 1 extending in the Y-axis direction and connected to an upper portion of the support column 1523 a , and a trunk part 1523 b 2 extending to the left from a rear end portion of the base part 1523 b 1 .
  • a swing support shaft 561 protrudes in the X-axis direction.
  • a bearing 562 that rotatably support the swing support shaft 561 is attached to an upper portion of the support column 1523 a .
  • the arm 1523 b is supported by the bearing 562 via the swing support shaft 561 so as to be rotatable about the rotation axis A 2 extending in the X-axis direction.
  • the bearing 562 is disposed such that the rotation axis A 2 passes through the contact position P. That is, the rotation axis A 2 is a straight line perpendicularly passing through the tread surface of the test wheel W.
  • the swing support shaft 561 and the bearing 562 form a part of the attack angle applying mechanism 56 .
  • the attack angle applying mechanism 56 includes a motor 564 , and a motion converter 563 that converts rotational motion of the motor 564 into a linear motion in the Z-axis direction.
  • the motor 564 in the present embodiment is an AC servo motor, other types of motor capable of controlling driving amount (rotation angle), such as a DC servo motor or a stepping motor, may be used as the motor 564 .
  • the motion converter 563 in the present embodiment is a feed screw mechanism such as a ball screw, other types of motion converter may be used.
  • the screw shaft of the motion converter 563 is rotatably supported by a pair of bearings, and one end of the screw shaft is connected to a shaft of the motor 564 via a bevel gear.
  • the screw shaft of the motion converter 563 may be directly connected to the shaft of the motor 564 .
  • the motor 564 and the motion converter 563 are attached to a swing frame coupled to the third movable base 522 C via a hinge having a rotation shaft extending in the X-axis direction so as to be rotatable (i.e., swingable) within a predetermined angular range about the rotation shaft of the hinge.
  • a nut (linearly moving part) of the motion converter 563 is coupled to the arm 1523 b of the support frame 1523 via a hinge having a rotation shaft extending in the X-axis direction so as to be swingable about the rotation shaft of the hinge.
  • the hinge attached to the arm 1523 b moves together with the nut substantially in the Z-axis direction. Accordingly, the test wheel W supported by the arm 1523 b together with the arm 1523 b rotates about the rotation axis A 2 passing through the contact position P (in other words, a straight line perpendicular to the tread surface of the test wheel), whereby an attack angle is given.
  • the motor 564 is connected to the controller 70 via a servo amplifier 564 a .
  • Phase information of the shaft detected by a rotary encoder RE embedded in the motor 564 is input to the controller 70 through the servo amplifier 564 a.
  • the controller 70 calculates the current value of the attack angle based on the signal of the rotary encoder RE embedded in the motor 564 .
  • the controller 70 controls the driving of the motor 564 based on setting data of the attack angle input through the interface 90 and the current value of the attack angle so that a set attack angle is given to the test wheel W.
  • the linearly moving part 532 a of the motion converter 532 of the wheel load applying mechanism 53 is fixed to the support column 1523 a of the support frame 1523 via the wheel load detector 533 .
  • the linearly moving part 532 a of the motion converter 532 is disposed so that the center line thereof coincides with the rotation axis A 2 . This prevents a large moment of force from being applied to the support frame 1523 when the wheel load is applied.
  • the wheel load applying mechanism 53 is provided on the wheel support 50 and is configured to adjust the wheel load by moving the test wheel W back and forth with respect to the rail wheel R.
  • the wheel load applying mechanism may be provided to the rail wheel support and the wheel load may be adjusted by moving the rail wheel R back and forth with respect to the test wheel W.
  • the rail wheel R is connected to the rotary driver 10 without the torque generator 20 therebetween, and the test wheel W is connected to the rotary driver 10 via the torque generator 20 .
  • the rail wheel R may be connected to the rotary driver 10 via the torque generator 20
  • the test wheel W may be connected to the rotary driver 10 without the torque generator 20 therebetween.
  • two torque generators 20 may be provided, and the rail wheel R may be connected to the rotary driver 10 via one torque generator 20 , and the test wheel W may be connected to the rotary driver 10 through another torque generator 20 .
  • a plurality of three component force sensors are provided to the wheel support 50 , and the measuring engine 80 measures the torque and wheel load acting on the test wheel W based on the detection results of the plurality of three component force sensors.
  • the torque and wheel load may be measured based on detection results of a plurality of two component force sensors or one component force sensors.
  • the function of the power distributor is incorporated in the rail wheel support 32 , but the power distributor may be separated from the rail wheel support 32 .
  • the first transmission section 30 may not be connected to the rail wheel support 32 , and the rotary driver 10 and the first transmission section 30 may be connected via additional power transmitter (e.g., winding transmission or gear transmission).
  • additional power transmitter e.g., winding transmission or gear transmission
  • the drive pulley 311 of the first belt mechanism 31 and the shaft of the rotary driver 10 to which a pulley or gear of the additional power transmitter is to be mounted function as the power distributor.
  • the fixed base 51 and the spindle 527 are coupled to each other via the lateral pressure applying mechanism 54 , the cant angle applying mechanism 55 , the wheel load applying mechanism 53 , and the attack angle applying mechanism 56 in this order.
  • the lateral pressure applying mechanism 54 , the cant angle applying mechanism 55 , the wheel load applying mechanism 53 , and the attack angle applying mechanism 56 may be connected in any order.

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  • General Physics & Mathematics (AREA)
  • Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
US18/048,319 2020-05-08 2022-10-20 Wheel test device with rail wheel to contact test wheel while test wheel is rotatably supported Active 2042-02-03 US12264989B2 (en)

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PCT/JP2021/017337 WO2021225133A1 (ja) 2020-05-08 2021-05-06 車輪試験装置

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US (1) US12264989B2 (enrdf_load_stackoverflow)
EP (1) EP4148409B1 (enrdf_load_stackoverflow)
JP (2) JP7338921B2 (enrdf_load_stackoverflow)
KR (1) KR20230008735A (enrdf_load_stackoverflow)
CN (1) CN115552212A (enrdf_load_stackoverflow)
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KR102622478B1 (ko) * 2023-06-13 2024-01-10 주식회사 엔지티 파워볼 테스트 장치를 포함하는 케이블 송출 시스템
CN117141548B (zh) * 2023-10-30 2024-01-30 成都铁安科技有限责任公司 一种用于轮对踏面损伤检测的平动装置

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CN115552212A (zh) 2022-12-30
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